US7198470B2 - Francis turbine - Google Patents

Francis turbine Download PDF

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Publication number
US7198470B2
US7198470B2 US10/867,207 US86720704A US7198470B2 US 7198470 B2 US7198470 B2 US 7198470B2 US 86720704 A US86720704 A US 86720704A US 7198470 B2 US7198470 B2 US 7198470B2
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Prior art keywords
crown
trailing edge
turbine
blades
rotating shaft
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Expired - Lifetime, expires
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US10/867,207
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US20050042104A1 (en
Inventor
Yasuyuki Enomoto
Kaneo Sugishita
Sadao Kurosawa
Toshiaki Suzuki
Takanori Nakamura
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Toshiba Corp
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Toshiba Corp
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Priority claimed from JP2003171108A external-priority patent/JP4094495B2/ja
Priority claimed from JP2003291266A external-priority patent/JP4280127B2/ja
Application filed by Toshiba Corp filed Critical Toshiba Corp
Assigned to KABUSHIKI KAISHA TOSHIBA reassignment KABUSHIKI KAISHA TOSHIBA ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ENOMOTO, YASUYUKI, KUROSAWA, SADAO, SUGISHITA, KANEO, NAKAMURA, TAKANORI, SUZUKI, TOSHIAKI
Publication of US20050042104A1 publication Critical patent/US20050042104A1/en
Assigned to KABUSHIKI KAISHA TOSHIBA reassignment KABUSHIKI KAISHA TOSHIBA TO CORRECT THE 5TH ASSIGNOR'S EXECUTION DATE ON DOCUMENT ID 102852956A RECORDED AT REEL/FRAME 015846/0278 Assignors: ENOMOTO, YASUYUKI, KUROSAWA, SADAO, NAKAMURA, TAKANORI, SUGISHITA, KANEO, SUZUKI, TOSHIAKI
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
    • F03B3/12—Blades; Blade-carrying rotors
    • F03B3/125—Rotors for radial flow at high-pressure side and axial flow at low-pressure side, e.g. for Francis-type turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/20—Rotors
    • F05B2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05B2240/301—Cross-section characteristics
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2250/00—Geometry
    • F05B2250/70—Shape
    • F05B2250/71—Shape curved
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/20—Hydro energy
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S416/00—Fluid reaction surfaces, i.e. impellers
    • Y10S416/02—Formulas of curves

Definitions

  • This invention relates to a Francis turbine that is used for a hydraulic turbine or a pump, and in particular, a Francis turbine having blades with an improved shape on a trailing edge.
  • a Francis turbine is used in a hydraulic machine, including a reversible pump-turbine, for power generation.
  • a conventional Francis turbine runner is described in U.S. Pat. No. 4,479,757.
  • This conventional Francis turbine runner includes blades whose inlet (a leading edge) shape is curved toward a direction opposite to a rotating direction of a turbine operation from a band side to a crown side.
  • This conventional Francis turbine runner includes blades whose inlet (a leading edge) shape is curved toward a rotating direction of a turbine operation from a band side to a crown side.
  • This conventional Francis turbine runner also includes blades whose outlet (a trailing edge) shape is curved toward a rotating direction of a turbine direction from a crown side to a band side.
  • a conventional reversible pump-turbine is described in Japanese Patent Publication (Kokai) No. 8-312517.
  • a runner of this conventional reversible pump-turbine has blades whose trailing edge is curved toward a direction opposite to a rotation direction of turbine operation from a middle point of the trailing edge to a band side.
  • secondary flow which is a flow not being along a flow line, distorts a pressure distribution on the blades and results in loss of hydraulic efficiency.
  • an advantage of an aspect of the present invention is to provide a Francis turbine with an improved shape of blades which can reduce cavitations generated on the surface of the blades or reduce the secondary flow around the blades.
  • one aspect of the present invention is to provide a Francis turbine that comprises a rotating shaft, a crown, which can rotate with the rotating shaft, a plurality of blades circumferentially arranged on the crown, each of which including an inner end as a trailing edge, and a band coaxially coupled with the crown by the blades, wherein the rotating shaft, the crown, the blades, and the band as a whole are driven by water and rotate toward a turbine direction during a turbine operation, wherein a projected profile of the trailing edge on a perpendicular plane, which is perpendicular to a center axis of the rotating shaft, is curved toward a direction opposite to the turbine direction at least in the crown side.
  • a Francis turbine runner which is rotatable around a rotation axis, that comprises a crown, which can rotate around the rotation axis, a plurality of blades circumferentially arranged on the crown, each of which including an inner end as a trailing edge, and a band coaxially coupled with the crown by the blades, wherein the crown, the blades, and the band as a whole are driven by water and rotate toward a turbine direction during a turbine operation, wherein a polar coordinate system defined by parameters r and ⁇ can be introduced on a perpendicular plane, which is perpendicular to the rotation axis, such that, (a) an origin is set at the rotation axis, (b) a positive direction of ⁇ is set to the turbine direction, wherein a projected profile of the trailing edge on the perpendicular plane is expressed in the polar coordinate system as, (c)
  • FIG. 1 is a plan view of a Francis turbine runner seen from a runner outlet side, according to a first embodiment of the invention.
  • FIG. 2 is a pressure distribution diagram around a surface of a blade near a center of a stream line in the turbine operation according to the first embodiment of the invention.
  • FIG. 3 is a plan view of a Francis turbine runner seen from the runner outlet side, according to the embodiment.
  • FIG. 4 is a characteristic diagram showing a relation between the minimum value of the pressure on the blade surface and a ⁇ value at the local minimum point on the projected profile of the trailing edge.
  • FIG. 5 is a plan view of the blades seen from an outlet side of the turbine with the band being removed from the runner.
  • FIG. 6 is a schematic exploded view of the conventional blade for the Francis turbine runner, schematically showing a result of a simulation of a pressure distribution on the suction surface during the turbine operation.
  • FIG. 7 is a schematic exploded view of the blade for the Francis turbine runner according to this embodiment, schematically showing a result of a simulation of a pressure distribution on the suction surface during the turbine operation.
  • FIG. 8 is a plan view of the blades seen from an outlet side of the turbine with the band being removed from the runner.
  • FIG. 9 is a characteristic diagram showing a relation among ⁇ b , ⁇ c , and hydraulic loss.
  • FIGS. 1 to 4 A first embodiment in accordance with the present invention will be explained with reference to FIGS. 1 to 4 .
  • FIG. 1 is a plan view of a Francis turbine runner 5 seen from a runner outlet side, according to a first embodiment of the invention.
  • FIG. 1 shows projected profiles of the outlet of the Francis turbine runner on a plane that is perpendicular to a rotation axis of the Francis turbine runner.
  • a plurality of runner blades (runner vanes) 6 are disposed in a circumferential array on a crown 7 .
  • a head side of the runner blade 6 is supported by the crown 7 at a crown edge 13 (also referred to as a crown connecting point).
  • a bottom side of the runner blade 6 is supported by a band 8 at a band edge 14 (also referred to as a band connecting point).
  • FIG. 1 is a plan view of a Francis turbine runner 5 seen from a runner outlet side, according to a first embodiment of the invention.
  • FIG. 1 shows projected profiles of the outlet of the Francis turbine runner on a plane that is perpendicular to a rotation axis of the Francis
  • FIG. 1 shows the Francis turbine runner 5 having eight runner blades 6 disposed therein.
  • band 8 is coaxially coupled to crown 7 by blades 6 and a rotation shaft (not shown) is connected at the center of crown 7 .
  • Francis turbine runner 5 is driven and rotates around a rotation axis, which is corresponding to the center of crown 7 where rotating shaft 28 is connected, toward a turbine direction during the turbine operation.
  • a rotation direction during the turbine operation is referred to as the turbine direction.
  • trailing edge 12 An inner end of blade 6 is referred to as a trailing edge 12 , since water flows out from the inner ends of blades 6 during the turbine operation.
  • trailing edge 12 of blade 6 is projected on a plane perpendicular to the rotation axis, trailing edge 12 is formed to be concave on the projected plane with respect to the turbine direction.
  • the turbine direction is shown as counterclockwise, trailing edge 12 of the runner blade 6 is formed to be concave left.
  • a projected profile of the trailing edge 12 on the plane is curved toward a direction opposite to the turbine direction, and formed to be convex with respect to the direction opposite to the turbine direction.
  • FIG. 2 is a pressure distribution diagram around a surface of runner blade 6 near a center of a stream line in the turbine operation according to the first embodiment of the invention.
  • a solid line is a conventional pressure distribution curve S 1 ; and a dotted line is a pressure distribution curve S 2 according to the first embodiment of the invention.
  • the horizontal axis indicates a position along the blade from a leading edge to a trailing edge.
  • the difference of blade pressure between a pressure surface and the suction surface of blade 6 is reduced compared with the conventional pressure distribution curve S 1 .
  • Pressure at the suction side surface of the blade is relatively high, and the minimum value of the pressure on the blade surface is not less than a saturation vapor pressure at which the cavitation is generated. This shows that the cavitation is hardly generated in Francis turbine runner 5 according to the embodiment, even at a high-flow operation point at which flow velocity in the Francis turbine runner 5 increases and the pressure on the runner-blade surface is relatively reduced.
  • the cavitation is hardly generated compared with the conventional one, even in the turbine operation with a larger flow rate. Therefore hydraulic efficiency may be improved. Or it may be operated in a wide operation range.
  • FIG. 3 is a plan view of Francis turbine runner 5 seen from the runner outlet side, according to the embodiment.
  • the same symbols are used to indicate corresponding features as in FIG. 1 . Detailed descriptions may be omitted for the same component as referred to in FIG. 1 .
  • FIG. 3 shows projected profiles of the outlet of Francis turbine runner 5 on the plane that is perpendicular to the rotation axis of Francis turbine runner 5 , a polar coordinates system using parameters r and ⁇ can be introduced such that:
  • an origin is defined as at the center axis of the rotating shaft, which is corresponding to the center of crown 7 ,
  • the projected profile of the trailing edge 12 on the perpendicular plane can be expressed as a function of r and ⁇ , in which r means a distance from the center of crown 7 . Since the positive direction of ⁇ is set to the turbine direction, the function satisfies:
  • a reference line of the angle ⁇ which means an origin of ⁇ ( ⁇ equals zero)
  • a straight line radial straight line
  • the projected profile of trailing edge 12 of blade 6 has a same angle ⁇ , which equals zero, at each of an inner circumference edge (band connecting point 14 ) and an outer circumference edge (crown connecting point 13 ).
  • band connecting point 14 exists on the radial straight line, which connects between the center of crown 7 and crown connecting point 13 .
  • the projected profile of trailing edge 12 satisfies: ⁇ 0 from crown connecting point 13 to band connecting point 14 .
  • a point that has the minimum value of ⁇ on the projected profile of trailing edge 12 is a local minimum point, where the value of ⁇ is locally minimized.
  • the function of the projected profile satisfies:
  • FIG. 4 is a characteristic diagram showing a relation between the minimum value of the pressure on the blade surface and a ⁇ value (referred to as ⁇ min) at the local minimum point on the projected profile of trailing edge 12 .
  • ⁇ min a ⁇ value
  • Zr indicates the number of blades 6 shown in FIGS. 1 and 3 .
  • a minimum value of ⁇ along the projected profile which is corresponding to the value of ⁇ at the local minimum point, is preferably in a range of:
  • the minimum value of the pressure on the blade surface becomes large, therefore the pressure may become not less than the saturation vapor pressure, at which the cavitations are generated.
  • the Francis turbine may be operated in an area where the cavitations are generated on the blade surface of the conventional Francis turbine.
  • FIGS. 5 to 9 A second embodiment in accordance with the invention will be explained referring to FIGS. 5 to 9 .
  • FIG. 5 is a plan view of the blades seen from an outlet side of the turbine (band side) with the band being removed from the runner.
  • a symbol 20 indicates a Francis turbine runner.
  • a symbol 21 indicates a blade
  • a symbol 22 indicates a crown.
  • Francis turbine runner 20 includes crown 22 , a plurality of blades 21 and a band (not shown).
  • a symbol 24 indicates a leading edge, which is an outer end of blade 21 , in which water comes during the turbine operation.
  • a symbol 31 indicates a trailing edge, which is an inner end of blade 21 , where water flows out during the turbine operation.
  • a symbol 28 indicates a rotating shaft (spindle) connected to crown 22 .
  • FIG. 5 shows projected profiles of blades 21 of Francis turbine runner 20 on a plane that is perpendicular to the rotation axis of the Francis turbine runner 20 .
  • a symbol 25 indicates a band connecting point, where the band and trailing edge 31 are connected, while a symbol 26 indicates a crown connecting point, where crown 22 and trailing edge 31 are connected.
  • the projected profile of a trailing edge 31 of blade 21 on the plane perpendicular to the rotation axis CL of the spindle (rotation shaft) 28 is formed to be concave in shape in the turbine direction from crown connecting point 26 (inner circumference side), and is formed in a sigmoid curve pattern that is convex in the turbine direction toward band connecting point 25 (outer circumference side).
  • a projected profile of the trailing edge 31 on the plane is curved toward a direction opposite to the turbine direction, and formed to be convex with respect to the direction opposite to the turbine direction at crown 22 side (near crown connecting point 26 ).
  • Band connecting point 25 exists on a radial straight line, which connects between rotation axis CL and crown connecting point 26 . In other words, both ends of the projected profile of trailing edge 31 are located on the radial straight line.
  • a polar coordinates system using parameters r and ⁇ also can be introduced such that:
  • an origin is defined as at the center axis CL of the rotating shaft 28 , which is corresponding to rotation center ⁇ ,
  • the projected profile of trailing edge 31 of blade 21 is configured such that it satisfies:
  • the projected profile may preferably be formed to have values of ⁇ that satisfies:
  • the points that satisfy equation (3) are a local minimum point M 1 and a local maximum point SM 1 shown in FIG. 5 .
  • local minimum point M 1 is the point on the projected profile that satisfies:
  • trailing edge 31 is configured in the sigmoid curve SC as a whole.
  • FIG. 6 is a schematic exploded view of the conventional blade for the Francis turbine runner, schematically showing a result of a simulation of a pressure distribution on the suction surface during the turbine operation.
  • a symbol 7 is a blade
  • a symbol 18 is a trailing edge
  • a symbol 14 is a band (band side root)
  • a symbol 15 is a crown (crown side root).
  • a symbol SFL indicates stream line (line of flow)
  • a symbol EP indicates a constant pressure line.
  • a projected profile of trailing edge 18 on the plane perpendicular to the rotation axis is formed as a radial straight line from crown 15 to band 14 .
  • pressure distribution is distorted around “X” region, which means that a flow toward band side root 14 is generated in the “X” region.
  • the flow toward band side root 14 around the “X” region is corresponding to secondary flow.
  • the reason for pressure distortion around the “X” region may be due to a difference of pressure between the leading edge and trailing edge 18 along stream line SFL being inconsistent between the band 14 side and the crown 15 side. In other words, the pressure difference along stream line SFL of crown 15 side is larger than that of band 14 side.
  • the pressure difference between the leading edge and the trailing edge can be enlarged by shortening the length of the blade.
  • the length of the blade 21 is enlarged in crown 22 side and shortened in band 23 side compared to the radial straight line, which connects between rotation axis CL and crown connecting point 26 . This may make the pressure difference between the leading edge and the trailing edge consistent between band 23 side and crown 22 side, and contribute to dissolve the pressure distortion, which is seen in “X” region of FIG. 6 .
  • FIG. 7 is a schematic exploded view of the blade for the Francis turbine runner according to this embodiment, schematically showing a result of a simulation of a pressure distribution on the suction surface during the turbine operation.
  • a symbol SFL indicates stream line (line of flow) and a symbol EP indicates a constant pressure line.
  • Trailing edge 31 of the runner blade 21 is configured in the sigmoid curve SC as a whole.
  • the pressure distortion found near leading edge 13 of the band side root 14 in FIG. 6 is not found. This means a flow in a direction different from stream line SFL is hardly generated, resulting in reduction of the secondary flow. Reduction of the secondary flow on the suction surface may improve hydraulic efficiency of the Francis turbine runner. Especially, since there is no pressure distortion at the suction side surface, the turbine efficiency in partial load operation of the Francis turbine may be improved.
  • FIG. 8 is a plan view of the runner blade seen from the outlet side of the turbine (band side) with the band being removed as in FIG. 5 .
  • the same components as in FIG. 5 are marked with the same symbols and are not be described in detail.
  • FIG. 8 corresponds to the projected drawing in which trailing edge 31 of blade 21 is projected on the plane perpendicular to the rotation center CL of the spindle (rotation axis) 28 .
  • the polar coordinates system using parameters r and ⁇ also can be introduced.
  • the value of ⁇ at crown connecting point 26 is defined as zero
  • the value of ⁇ at local minimum point M 1 and local maximum point SM 1 are defined as ⁇ c and ⁇ b respectively.
  • the circumferential position of crown connecting point 26 equals to that of band connecting point 25 .
  • ⁇ of the band connecting point 25 and ⁇ of crown connecting point 26 is the same, which equals zero in this case.
  • ⁇ b corresponds to an angle between line HL and a line R 1 L, which connects between rotation center CL and local maximum point SM 1 .
  • ⁇ c corresponds to an angle between line HL and a line R 2 L, which connects between rotation center CL and local minimum point M 1 .
  • FIG. 9 is a characteristic diagram showing a relation among ⁇ b , ⁇ c , and hydraulic loss. Hydraulic loss is illustrated as curves connecting points of equal loss in the various values of ⁇ c and ⁇ b .
  • the vertical axis is the value of ⁇ b
  • the horizontal axis is the value of ⁇ c
  • Zr is the number of blades 21 of runner 20
  • the dotted lines are constant loss curves, which show that the hydraulic loss is smaller at a more inner side than the periphery.
  • values of ⁇ c and ⁇ b may be preferably,

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Turbines (AREA)
US10/867,207 2003-06-16 2004-06-15 Francis turbine Expired - Lifetime US7198470B2 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2003171108A JP4094495B2 (ja) 2003-06-16 2003-06-16 フランシス形ランナ
JP2003-171108 2003-06-16
JP2003-291266 2003-08-11
JP2003291266A JP4280127B2 (ja) 2003-08-11 2003-08-11 フランシス形ランナ

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US20050042104A1 US20050042104A1 (en) 2005-02-24
US7198470B2 true US7198470B2 (en) 2007-04-03

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BR (1) BRPI0401970B1 (pt)
DE (1) DE102004029109A1 (pt)
NO (1) NO332510B1 (pt)

Cited By (9)

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US20110206518A1 (en) * 2008-09-05 2011-08-25 Alstom Hydro France Francis-type runner for a hydraulic machine, hydraulic machine including such a runner, and method for assembling such a runner
USD652794S1 (en) 2010-11-12 2012-01-24 Verterra Energy Inc. Turbine
US20120156046A1 (en) * 2010-12-21 2012-06-21 Merritt Brent J Turbine rotor for air cycle machine
US20120156026A1 (en) * 2010-12-21 2012-06-21 Merritt Brent J Air cycle machine compressor rotor
WO2013059935A1 (en) 2011-10-23 2013-05-02 Andritz Hydro Ltd. Compact blade for runner of francis turbine and method for configuring runner
US8487468B2 (en) 2010-11-12 2013-07-16 Verterra Energy Inc. Turbine system and method
WO2016011537A1 (en) * 2014-07-23 2016-01-28 Andritz Hydro Ltd. Francis turbine with short blade and short band
US9874197B2 (en) 2015-10-28 2018-01-23 Verterra Energy Inc. Turbine system and method
US10151321B2 (en) 2013-10-16 2018-12-11 United Technologies Corporation Auxiliary power unit impeller blade

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CA2488714A1 (en) * 2004-11-30 2006-05-30 General Electric Canada Runner for francis type hydraulic turbine
JP4751165B2 (ja) * 2005-10-12 2011-08-17 株式会社東芝 フランシス形ポンプ水車
US20070231141A1 (en) * 2006-03-31 2007-10-04 Honeywell International, Inc. Radial turbine wheel with locally curved trailing edge tip
FR3003309A1 (fr) * 2013-03-18 2014-09-19 Alstom Hydro France Roue de type francis pour machine hydraulique, machine hydraulique equipee d'une telle roue et installation de conversion d'energie comprenant une telle machine hydraulique
JP6132708B2 (ja) * 2013-08-23 2017-05-24 株式会社東芝 水車ランナおよび水車
IT201900010632A1 (it) * 2019-07-02 2021-01-02 Dab Pumps Spa Girante perfezionata per pompa centrifuga, particolarmente per pompa del tipo a girante arretrata, e pompa con una simile girante
CN113277045B (zh) * 2021-05-20 2022-05-20 南昌航空大学 一种辐流式水下推进器

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US9175662B2 (en) * 2008-09-05 2015-11-03 Alstom Renewable Technologies Francis-type runner for a hydraulic machine, hydraulic machine including such a runner, and method for assembling such a runner
US9291146B2 (en) 2010-11-12 2016-03-22 Verterra Energy Inc. Turbine system and method
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US20120156046A1 (en) * 2010-12-21 2012-06-21 Merritt Brent J Turbine rotor for air cycle machine
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US8523530B2 (en) * 2010-12-21 2013-09-03 Hamilton Sundstrand Corporation Turbine rotor for air cycle machine
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WO2013059935A1 (en) 2011-10-23 2013-05-02 Andritz Hydro Ltd. Compact blade for runner of francis turbine and method for configuring runner
US9605647B2 (en) 2011-10-23 2017-03-28 Andritz Hydro Ltd. Compact blade for runner of Francis turbine and method for configuring runner
US10151321B2 (en) 2013-10-16 2018-12-11 United Technologies Corporation Auxiliary power unit impeller blade
WO2016011537A1 (en) * 2014-07-23 2016-01-28 Andritz Hydro Ltd. Francis turbine with short blade and short band
RU2687188C2 (ru) * 2014-07-23 2019-05-07 Андритц Гидро Лтд. Турбина фрэнсиса с короткими лопастями и коротким ободом
US10465647B2 (en) 2014-07-23 2019-11-05 Andritz Hydro Ltd. Francis turbine with short blade and short band
US9874197B2 (en) 2015-10-28 2018-01-23 Verterra Energy Inc. Turbine system and method

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CN1329630C (zh) 2007-08-01
NO20042528L (no) 2004-12-17
US20050042104A1 (en) 2005-02-24
DE102004029109A1 (de) 2005-02-03
BRPI0401970A (pt) 2005-01-25
NO332510B1 (no) 2012-10-08
CN1573019A (zh) 2005-02-02

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